Continuously Variable Transmission

ABSTRACT

The invention relates to a continuously variable transmission. The continuously variable transmission comprises an outer rotary part, an inner rotary part which is arranged in the outer rotary part such that the inner and/or the outer rotary part are rotatable relative to one another, several coupling mechanisms for coupling the inner and outer rotary part with one another, an adjustment device for eccentric adjustment of the inner and outer rotary part relative to one another, a pump for delivering a lubricant into the transmission along a shell surface of the inner rotary part, and sealing elements which are arranged on the inner rotary part in the coupling mechanisms, or nozzles for delivering a predetermined amount of lubricant to the particular coupling mechanism.

BACKGROUND

The invention relates to a continuously variable transmission. Atransmission in which a rotational speed of a rotary part is convertedinto a rotational speed of another rotary part can also be constructedas a continuously variable transmission. In such a transmission theconversion ratio of the rotational speeds is continuously variable in apredetermined range. Continuously variable transmissions are known, forexample, from DE 102 34 463 A1 or DE 36 05 211 A1, each of which,however, allow only low torques.

SUMMARY

To solve this problem the inventor of the present application hasdeveloped a continuously variable transmission in which an outer rotarypart or an inner rotary part can rotate around rotational axes which areparallel to one another and can be displaced eccentrically relative toone another. Such a continuously variable transmission is suitable forhigher torques than in the prior art. However, there is the need here tooptimise the continuously variable transmission for long-term operationor to increase its life.

The object of the present invention is therefore to provide acontinuously variable transmission which solves the problems of theprior art. In particular, a continuously variable transmission in whichhigh torques of the order of from approx. 100 Nm up to several mega-Nmin long-term operation are possible is to be provided.

The object is achieved by a continuously variable transmission havingthe features of claim 1. The continuously variable transmissioncomprises an outer rotary part, an inner rotary part which is arrangedin the outer rotary part such that the inner and/or the outer rotarypart are rotatable relative to one another, several coupling mechanismsfor coupling the inner and outer rotary part with one another, anadjustment device for eccentric adjustment of the inner and outer rotarypart relative to one another, a pump for delivering a lubricant into thetransmission along a shell surface of the inner rotary part, and sealingelements which are arranged on the inner rotary part in the couplingmechanisms, or nozzles for delivering a predetermined amount oflubricant to the particular coupling mechanism.

With the continuously variable transmission, a smooth-running operationof the continuously variable transmission can be realised even at highrotational speeds and/or torques. Furthermore, the life of thecontinuously variable transmission is improved compared with theconfigurations of the prior art to date.

By a light-weight and inexpensive configuration of the transmission,furthermore, the operating properties can be improved and the productioncosts lowered.

The present invention therefore furthermore relates to a continuouslyvariable transmission having an outer rotary part, an inner rotary partwhich is arranged in the outer rotary part such that the inner and/orthe outer rotary part are rotatable relative to one another, severalcoupling mechanisms for coupling the inner and outer rotary part withone another and an adjustment device for eccentric adjustment of theinner and outer rotary part relative to one another.

Advantageous further configurations of the invention are described inthe dependent claims.

In one advantageous embodiment the continuously variable transmissionfurthermore comprises a housing for accommodating the continuouslyvariable transmission, wherein particularly preferably the pump fordelivering the lubricant is arranged in a circulation into and/or fromthe housing.

According to a further advantageous variant the outer rotary part hasdiscs spaced apart by bearing bolts for the coupling mechanisms.

According to a further advantageous embodiment the outer rotary part hastwo casings fixed to one another, which are spaced apart by bearingbolts for the coupling mechanisms.

In a further advantageous embodiment of the continuously variabletransmission one of the coupling mechanisms has an inner coupling modulewhich is arranged on the inner rotary part and an outer coupling modulewhich is arranged on the outer rotary part, wherein particularlypreferably the inner coupling module has a mass balancing bolt forbalancing a mass of a bearing bolt of at least one coupling module,preferably just one coupling module and particularly preferably theinner coupling module or the outer coupling module, with which bearingbolt the inner and outer coupling module can be fixed to one anotherrotatably/pivotably, similarly to a knee joint.

Furthermore, in a further advantageous embodiment the inner couplingmodule has at least one slot for receiving carbon fibres wound bylamination with pretension.

In a further advantageous embodiment the inner rotary part has at leastone wound metal sheet. Particularly preferably, the at least one woundmetal sheet is arranged here in a tube.

In the continuously variable transmission, in a further advantageousembodiment a lower end of a sprag is concave in construction, the spragserving to support one of the coupling mechanisms on the inner rotarypart. By this construction the life can be increased, since even with acertain removal of material by wear a reliable contact with the spragstill exists. Preferably, the correspondingly other contact surface ofthe sprag located at the upper end of the sprag is convex inconstruction.

Preferably, the inner contact surface, that is to say the contactsurface of the sprag in the direction of the inner rotary part, isconcave in construction and the outer contact surface, that is to saythe contact surface of the sprag in the direction of the outer rotarypart, is convex in construction. Preferably, the course of at least onecontact surface can follow a logarithmic spiral.

Furthermore, in a further advantageous embodiment of the continuouslyvariable transmission a bearing position for an adjusting element of theadjustment device is arranged in the axial direction centrally on abearing and guiding module, which serves to support the outer rotarypart.

In a further advantageous embodiment the outer and inner coupling modulecan be swivelled by an angle with respect to one another, andparticularly preferably this angle is always less than 180°. By thismeans the coupling mechanism cannot fold over.

Preferably, the geometric connection between the middle point of theinner rotary part and a first linkage of the inner coupling module onthe one hand and the geometric connection between the first linkage ofthe inner coupling module and a second linkage of the outer couplingmodule on the other hand enclose an angle which is less than 180°,preferably less than 179°, 178°, 177°, 176° or 175°. Preferably, theangle just mentioned is, advantageously additionally to the abovemaximum limit, greater than 20° and particularly preferably greater than30°. In this context the articulated axis at which the inner and theouter coupling module are connected pivotably to one another, forexample a bearing bolt, preferably corresponds to the first linkage ofthe inner coupling module, and particularly preferably the bearing whichserves as an inner bearing for the outer coupling module and as an outerbearing for the inner coupling module corresponds to the first linkageof the inner coupling module. The second linkage of the outer couplingmodule preferably corresponds to the bearing which serves as an outerbearing for the outer coupling module.

In a further advantageous embodiment the eccentricity of the couplingmechanism and/or of the outer rotary part relative to the inner rotarypart and/or the pivotability is limited with the adjustment device withstops. Preferably, this is effected by stops in the coupling mechanism,particularly preferably by a limitation of the relative pivotabilitybetween the inner and outer coupling module.

In a further advantageous embodiment the eccentricity of the couplingmechanism between the housing and a bearing and guiding module whichserves to support the outer rotary part is limited by stops.

In a further advantageous embodiment stops of the coupling mechanism areformed in the articulated axes from an outer bearing for the outercoupling module and/or from a bearing which serves as an inner bearingfor the outer coupling module and as an outer bearing for the innercoupling module.

In a further advantageous embodiment the outer bearing for the outercoupling module and the other bearing which serves as an inner bearingfor the outer coupling module and as an outer bearing for the innercoupling module each comprise in each case two parts, which arepreferably configured as two bearings which are connected with oneanother rotatably or rigidly.

By a coupling mechanism of such a configuration the sinus function of amovement of the coupling mechanism is deformed such that it approachesthe ideal of a rectangular function. As a result a uniform rotarymovement is obtained at the output drive.

Preferably, the inner and outer coupling modules move not around onepivotal point but around two pivotal points. Particularly preferably,the angle between the two parts of the outer bearing and of the otherbearing is in each case constant.

In a further advantageous embodiment an oscillation generator having adifferential transmission is interconnected in the continuously variabletransmission. Preferably, this is realised by a planetary transmission.Particularly preferably, in this the ratio of the rotational speed ofthe sun wheel, which is connected to the output drive of the oscillationgenerator, to the ring gear is 5:1. Preferably, an oscillation generatoris understood as meaning the inner or the outer rotary part or thecoupling mechanism(s).

In a further advantageous embodiment a lubricant stream exists in theaxial direction along the shell surface of the inner rotary part.Particularly preferably, a lubricant supply is provided between theinner rotary part and the coupling mechanisms, advantageously betweenthe inner rotary part and the inner coupling module(s).

It is also possible to transfer the lubricant supply according to theinvention to conventional continuously variable transmissions.

Further possible implementations of the invention also includecombinations which are not mentioned explicitly of features orembodiments which are described above or in the following with respectto the examples. In this context the person skilled in the art will alsoadd individual aspects as improvements or additions to the particularbasic form of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention is described in more detail in the following withreference to the attached drawing and with the aid of examples.

FIG. 1 illustrates a three-dimensional view of a continuously variabletransmission according to a first example;

FIG. 2 illustrates a plan view of a continuously variable transmissionaccording to the first example;

FIG. 3 illustrates a section view of the continuously variabletransmission according to the first example;

FIG. 4 illustrates a plan view of an outer rotary part of thecontinuously variable transmission according to a second example;

FIG. 5 illustrates a section along a line A-A in FIG. 4 through theouter rotary part of the continuously variable transmission according tothe second example;

FIG. 6 illustrates a section along a line C-C in FIG. 4 through theouter rotary part of the continuously variable transmission according tothe second example;

FIG. 7 illustrates a plan view of an outer rotary part of thecontinuously variable transmission according to a third example;

FIG. 8 illustrates a section along a line A-A in FIG. 7 through theouter rotary part of the continuously variable transmission according tothird example;

FIG. 9 illustrates a section parallel to the radius through an innerrotary part of the continuously variable transmission according to afifth example;

FIG. 10 illustrates a longitudinal section through the inner rotary partof the continuously variable transmission according to the fifthexample;

FIG. 11 includes diagrams to illustrate a construction of a couplingmechanism of the continuously variable transmission according to a sixthexample;

FIG. 12 includes diagrams to illustrate a construction of a couplingmechanism of the continuously variable transmission according to a sixthexample;

FIG. 13 includes a diagram of a construction of a coupling mechanism ofthe continuously variable transmission according to a seventh example;

FIG. 14 illustrates views of an inner coupling module of thecontinuously variable transmission according to an eighth example;

FIG. 15 illustrates views of an inner coupling module of thecontinuously variable transmission according to an eighth example;

FIG. 16 illustrates views of an inner coupling module of thecontinuously variable transmission according to an eighth example;

FIG. 17 illustrates views of an outer coupling module of thecontinuously variable transmission according to the eighth example;

FIG. 18 illustrates views of an outer coupling module of thecontinuously variable transmission according to the eighth example;

FIG. 19 illustrates views of variants for a sprag of the continuouslyvariable transmission according to the eighth example;

FIG. 20 illustrates views of variants for a sprag of the continuouslyvariable transmission according to the eighth example;

FIG. 21 illustrates views of further variants for a sprag of thecontinuously variable transmission according to the eighth example;

FIG. 22 illustrates views of further variants for a sprag of thecontinuously variable transmission according to the eighth example;

FIG. 23 illustrates variants for an axial securing of a bolt or a shaftof the continuously variable transmission according to the eighthexample;

FIG. 24 illustrates variants for an axial securing of a bolt or a shaftof the continuously variable transmission according to the eighthexample;

FIG. 25 illustrates variants for an axial securing of a bolt or a shaftof the continuously variable transmission according to the eighthexample;

FIG. 26 illustrates variants for an axial securing of a bolt or a shaftof the continuously variable transmission according to the eighthexample;

FIG. 27 illustrates variants for a radial securing against twisting of abolt or a shaft of the continuously variable transmission according tothe eighth example;

FIG. 28 illustrates variants for a radial securing against twisting of abolt or a shaft of the continuously variable transmission according tothe eighth example;

FIG. 29 illustrates variants for a radial securing against twisting of abolt or a shaft of the continuously variable transmission according tothe eighth example;

FIG. 30 illustrates variants for a radial securing against twisting of abolt or a shaft of the continuously variable transmission according tothe eighth example;

FIG. 31 illustrates variants for a radial securing against twisting of abolt or a shaft of the continuously variable transmission according tothe eighth example and

FIG. 32 illustrates a section view of a preferred embodiment of thecontinuously variable transmission to illustrate a variant for alubricant supply.

In the figures elements which are identical or of identical function aregiven the same reference symbols, unless stated otherwise.

DETAILED DESCRIPTION

FIG. 1 shows a base plate 1, on which a continuously variabletransmission 10 is mounted without a housing. The base plate 1 can alsobe configured differently as required. The transmission 10 has a firstbearing and guiding module 11 and a second bearing and guiding module12, and an inner rotary part 13, which is rotatable around its axis A1,an outer rotary part 14 and an adjusting element 15, which is guided ina guiding element 16 and is rotatably supported with a bearing 17.

As shown in FIG. 2, in which the base plate 1 is not shown, thecontinuously variable transmission 10 furthermore has several couplingmechanisms 18 and a housing 19, which is arranged around the secondbearing and guiding module 12, and optionally also an adjustment drivedevice 20 and a bearing position 21 for the adjusting element 15. Afixing flange for the second bearing and guiding module 12 can beintegrated in the housing 19. In the continuously variable transmission10 according to FIG. 1 and FIG. 2 the coupling mechanisms 18 couple theinner rotary part 13, which is configured as a shaft, and the outerrotary part 14, which is configured as a hollow cylinder. Conversion ofthe rotational speed of the inner rotary part 13 into a rotational speedof the outer rotary part 14 or vice versa can thus be performed. In thecase shown in FIG. 1 and FIG. 2 the ratio of the rotational speeds ofthe inner rotary part 13 and outer rotary part 14 is 1:1, so that thecontinuously variable transmission 10 implements neither an upwardsconversion nor a downwards conversion. The inner and outer rotary part13, 14 are rotatable with the same rotational speed in this case.

In the continuously variable transmission 10 the first bearing andguiding module 11 serves to support and guide the inner rotary part 13.The inner rotary part 13 is rotatably supported on the first bearing andguiding module 11 and arranged in the outer rotary part 14, which isarranged outside around the inner rotary part 13. The first bearing andguiding module 11 ensures that the inner rotary part 13 can implementexclusively a rotary movement around its axis A1.

In contrast, the second bearing and guiding module 12 serves to supportand guide the outer rotary part 14. The second bearing and guidingmodule 12 has, like the outer rotary part 14, a hollow cylindrical ordrum-like shape and supports the outer rotary part 14 on its outside.The second bearing and guiding module 12 supports the outer rotary part14 pivotably with respect to the inner rotary part 13. The pivotingadjustment can be performed with the adjusting element 15 in the form ofa threaded spindle. The adjusting element 15 here can be moved upwardsin the guiding element 16 in FIG. 1 or FIG. 2, in order to establish aconversion C>1 in the continuously variable transmission 10. However, ifthe adjusting element 15 is moved downwards in the guiding element 16 inFIG. 1 or FIG. 2, a conversion C>1 can likewise be established in thecontinuously variable transmission 10. In this context the outer rotarypart 14 can be adjusted such that the inner rotary part 13 is arrangedeccentrically to the axis of the outer rotary part 14. In such cases theconversion of the continuously variable transmission 10 is not equal to1:1. In particular, it has been found in experiments that the conversionfrom the outside inwards, that is to say from the outer rotary part 14to the inner rotary part 13, is different to a conversion from theinside outwards, that is to say from the inner rotary part 13 to theouter rotary part 14. In particular, a three-dimensional pivotingmovement of the outer rotary part 14 can be realised with the adjustingelement 15. The points of the pivot bearing should lie as far apart aspossible.

As illustrated in FIG. 2, the adjusting element 15 can optionally alsobe moved with the adjustment drive device 20, which is configured as amotor and in particular as a spindle gear motor etc., or as a piston,such as, in particular, a double action hydraulic piston, a doubleaction pneumatic piston etc. For this, the adjustment drive device 20,more accurately the bearing position 21 in FIG. 2, can also be arrangedin the axial direction of the second bearing and guiding module 12centrally on the second bearing and guiding module 12. The adjustmentdrive device 20 in FIG. 2 is consequently also arranged in the axialdirection centrally to the outer rotary part 14. In such an arrangementthe force transmission is particularly advantageous. However, thearrangement can also be at any point along the cylinder. Overall,however, it is to be taken into account that the points of the adjustingor pivot support should lie as far apart as possible in order to obtainthe highest possible torsional stability of the second bearing andguiding module 12 accompanying the housing 19.

According to the construction of the continuously variable transmission10 according to FIG. 2, the functional parts, such as second bearing andguiding module 12, outer rotary part 14, housing 19 have annular shapes.The reason for this is that approximately annular cylindrical parts canaccommodate extremely high torsion and flexural forces in their shellplane relative to their diameter. The inner rotary part 13 in FIG. 2 hasthe lowest diameter, but the greatest wall thickness. The wall thicknessof the individual functional parts decreases with increasing diameter ofthe individual functional parts. For this reason the wall thicknessescan be kept low, which independently of the material results in lowweight at maximum strength.

The annular gap 22 between the housing 19 and the second bearing andguiding module 12 shown in FIG. 2 is not absolutely necessary. Thehousing 19 can also be arranged directly adjacent to the second bearingand guiding module 12 at least in a part region.

FIG. 3 shows the continuously variable transmission 10 in a varianthaving six coupling mechanisms 18 in a longitudinal section. However,more or fewer coupling mechanisms 18 can also be present. The couplingmechanisms 18 are each arranged between two bars 141 of the outer rotarypart 14. The bars 141 each protrude outwards in the radial direction ofthe outer rotary part 14 in the direction of the first rotary part 13.For clarity, in FIG. 3 only some of the coupling mechanisms 18 and thebars 141 are provided with a reference symbol. In FIG. 3, furthermore,the first to fourth sealing elements 23, 24, 25, 26, a recess 27, abearing 28 to support the outer rotary part 14 and a bearing bolt 29 forthe coupling mechanisms 18 are shown. For clarity, in FIG. 3 only two ofthe second sealing elements 24 are provided with a reference symbol. Thecoupling mechanisms 18 are arranged around the inner rotary part 13 viaa sprag-type freewheel clutch or a radial support and furthermore areconnected to the outer rotary part 14. In the coupling system ofcoupling mechanisms 18 and sprag-type freewheel clutch or radialsupport, corresponding to their angles of action accompanying the massaccelerations during operation of the continuously variable transmission10, very high varying tensile and compressive forces of an order ofapprox. 4,000 N arise at 160 Nm output torque, these forces actingbetween the inner rotary part 13 and the outer rotary part 14. As aconsequence thereof, all the components of the continuously variabletransmission 10 must withstand these high forces. The outer rotary part14 is therefore divided on its inside with the bars 141 into annularchambers which have two tasks. On the one hand the bars 141 andtherefore the chambers give the outer rotary part 14 an extremely highradial stability and shape retention, on the other hand the annular bars141 form a receiver for supporting the coupling mechanisms 18.

Furthermore, the continuously variable transmission 10 in FIG. 3 has apump 30 which can pump a lubricant in the direction of an arrow 5, thatis to say in the axial direction, into the housing 19. In the directionof an arrow 6, that is to say in the radial direction, the pump 30 canpump the lubricant out of the housing 19. The pump 30 can thereforesupply all the bearing positions arranged around the inner rotary part13, and the coupling mechanisms 18 with lubricant in the axialdirection. As a result the temperatures of the continuously variabletransmission 10 can be kept low, so that as little friction as possibleis present. The lubricant 10 can be, in particular, oil.

As shown in FIG. 3, the lubricant is pumped by the pump 30 into theannular recess 27 axially and above the shell line of the inner rotarypart 13. Furthermore, the coupling elements 18 arranged in series aresealed off axially from one another and from the housing 19 with thefirst to fourth sealing elements 23, 24, 25, 26, so that the couplingsystem/bearing or clutch system/bearing furthest removed from thelubricant supply is also adequately supplied with lubricant. The sealingdescribed above is configured such that it is partially permeable to thelubricant in the radial direction.

The second sealing elements 24 are consequently arranged around theinner rotary part 13 in the axial direction of the inner rotary part 13.The second sealing elements 24 can be configured as thrust/sealingwashers which have furrows or channels or bores in the radial direction,which have the purpose of allowing a particular amount of lubricant toarrive at the coupling mechanisms 18 and the remaining bearingpositions. During operation of the continuously variable transmission 10the lubricant is delivered by the centrifugal force from the innerrotary part 13 outwards in the direction of the outer rotary part 14 andthe housing 19. At the housing inner wall the lubricant runs to thelowest point and can be sucked up from there by the pump 30 anddelivered out of the housing 19 in the direction of the arrow 6. Thecentrifugal force of the rotating parts thus distributes a portion ofthe lubricant effectively to the coupling mechanisms 18 and all otherbearing positions. The pump 30 can also be realised with gear wheels.

The continuously variable transmission 10 according to the first examplethus comprises a highly effective lubricant circulation in which theinner rotary part 14 is configured as a solid part. The inner rotarypart 14 has, for example, no oil supply bores, which represent aweakening of the shaft statics and from which rupture lines can start.This is a great advantage since the inner rotary part 14 is always theweakest member in the construction relative to all the other cylindricalcomponents of the continuously variable transmission 10. The reason forthis is that the inner rotary part 14 always has the smallest diameterwith respect to its span relative to the other cylindrical components,and therefore its flexing is the greatest.

For this reason the inner rotary part 14 can also be manufactured fromhigh performance materials, such as e.g. special steels etc., which havea very high tensile/compressive stress, or with the largest possiblediameters.

In a modification of the first example the coupling mechanisms 18 arearranged without an axial separation from the inner rotary part 13. Inthis case the second sealing elements 24 are omitted. Thelubricant-delivering furrows or channels or bores are then mounteddirectly laterally on the coupling mechanisms 18.

According to a further modification of the first example the lubricantcan be sprayed on to the coupling mechanism 18 through stationarynozzles on the housing 19. The nozzles can also be fixed on the secondbearing and guiding module 12. The coupling mechanism 18 has axiallubricant guiding slots on the side towards the outer rotary part 14,which allow the lubricant to be guided to the bearing positions.

In the continuously variable transmission 10 the operating rotationalspeed and the associated performance of the inner or outer rotary part13, 14 as an oscillation generator represents an important pillar. Thereis the possibility of driving the oscillation generator with severaltimes the input rotational speed and of correspondingly converting downthe output rotational speed with the same conversion C. For example 1:3input drive, 3:1 output drive.

Since the coupling mechanism 18 must rotate or shift more often relativeto the input rotational speed, the transmission torque per shift pulsefalls. That is to say the coupling systems shift more often with lowertorques according to the conversion. Oscillation generators with as faras possible constant high rotational speeds which as far as possiblehave no rotary imbalances should therefore be available. The furtherexamples show specific further configurations for this.

It is moreover to be noted that based on the phase angle of the inputrotational speed a pulse is generated according to the input conversion,that is to say e.g. the oscillation generator has six couplingmechanisms 18 which are arranged with a displacement of in each case 60°on the outer rotary part 14. This means at an input conversion of 1:3 apulse takes place every 20°, based on the phase angle of the inputrotational speed. Assuming that in the transmission 10 at a conversionC=1:1 the input drive rotational speed is the same as the output driverotational speed, the input conversion must be reversed again after theoscillation generator, that is to say 3:1. This means that starting fromthe abovementioned example with six coupling mechanisms 18, a pulsetakes place on the transmission output every 60°, only with thedifference that the oscillation generator had shifted the energy to betransmitted three times more often, accompanying a corresponding lowercoupling torque. Using this method the conversion range can be enlargedand the shifting torques of the coupling systems reduced.

In a continuously variable transmission 10 having a downstreamdifferential and zero passage the advantages have a particular effect.The extension of these properties represents the connecting of anoscillation generator having a differential transmission. If thearrangement is realised with a planetary transmission which has 20 teethon the sun wheel and 100 teeth on the ring gear, the sun wheel can beconnected to the output drive of the oscillation generator, whichrotates five times faster than the input rotational speed, the ring gearrotating once opposite to the input rotational speed. If the ring gearis driven on the outer teeth, an additional gear wheel is required. Ifthe ring gear is driven internally, this gear wheel is dispensed with.When the arrangement is set in operation at C=0 of the oscillationgenerator, the sun wheel rotates five times and the ring gear once inthe opposite direction. The consequence is that the planetary wheel setstands, which represents the transmission output drive. Starting fromthe abovementioned example of employing six coupling mechanisms 18, thepulse phase angle, 60° here, is divided by the factor of the powersplit, factor 5 here. From this it results that 60° divided by 5 equals12°. Since the reference level is zero, on the one hand the number ofpulses and conversion depends on the split ratio of the planetarytransmission, and on the other hand it depends on the extent to whichthe continuously variable transmission 10 is converted relative to therotational speed of an input drive machine, not shown.

According to a second example the outer rotary part 14 is modified, asshown in FIG. 4 to FIG. 6 and described below. The continuously variabletransmission 10 is otherwise constructed as in the first example.

In the present example, for the outer rotary part 14 discs 142, which inparticular are annular in configuration, are fixed on bearing bolts 144by means of fixing elements 143, such as screws, rods and nuts. Thefixing elements 143 are arranged on the ends of the bearing bolts 144.One of the discs 142 can have openings, the other can have threadedopenings. The number of discs 142 is determined by the number ofchambers formed by the bars 141. Furthermore, fixing elements 145, suchas screws, bars and nuts etc., and bearing bolts 146 are provided withrespect to the second bearing and guiding module 12. In FIG. 4 to FIG.6, as fixing elements 143, 145 in each case a rod with thread on its twoends is thus screwed with nuts. Alternatively, the rod can also beprovided with a thread only one of its two ends. The rod is arranged ina hollow cylindrical rotary part, the bearing bolt 144 or the bearingbolt 146. The bearing bolt 144 serves as a bearing of the outer part ofthe coupling mechanism 18, which part is also called outer couplingmodule in the following. The bearing bolt 146 serves as a bearing of thesecond bearing and guiding module 12. In FIG. 6 a support is moreoverprovided with a reference symbol 149.

In this embodiment of the outer rotary part 14 it is the aim to connectthe two annular discs 142 such that they cannot shift relative to oneanother. This construction, which is also called compressive stressconstruction, decisively increases the resistance to twisting andflexing of the two components, so that they acquire strength as if itwere a one-piece component which, in particular, is annular. Thisconstruction can be employed generally in the continuously variabletransmission 10, that is to say for all concentric parts of thecontinuously variable transmission 10.

Due to the absence of a shell plane the bearing bolts 144, 146 arebetter equipped against flexing. A higher instability can develop in thetorsional direction of the outer rotary part 14, which can becounteracted, for example, with in each case two opposite cross-bars.

As furthermore shown in FIG. 5, two discs 142 in the centre of the outerrotary part 14 are interlocked with one another with the aid of teeth147, 148 formed from a protrusion 147 and a groove 148, which areconfigured, for example, peripherally on the disc 142. The teeth 147,148 can also be trapezoidal or wavy.

A further measure for obtaining torsional rigidity is for additionalelements, in addition to the bearing bolts 144, to be employed accordingto the tube/rod principle and tensioned accordingly. In order to givethe annular discs 142 maximum stability at the lowest possible weight,embossed patterns/lines etc. can be pressed in over the area.

Furthermore, the support of the outer rotary part 14 should only belarge enough for swivelling or adjustment of the second bearing andguiding module 12 to be possible and for an annular connecting segmentfor an output drive gear wheel to be realisable.

Moreover, the cylinder formed by the outer rotary part 14 can have holeson its shell surface to reduce weight, so that a type of grid structureis formed. An extremely high torsion stability/flexural strength is thusachieved at a low component weight. According to a third example theouter rotary part 14 is modified as shown in FIG. 7 and FIG. 8 anddescribed in the following. The continuously variable transmission 10 isotherwise constructed as in the second example.

In the present example instead of the discs 142 of FIG. 4 to FIG. 6, twocasings 150, 151 are fixed to one another. In particular, the twocasings 159, 151 are screwed to one another. However, other suitabletypes of fixing are also conceivable.

Furthermore, in the present example in the outer rotary part 14 at leastsome of the bearing bolts 144 from FIG. 5 and FIG. 6 are formed from twoparts, namely tube 144A and rod 144B. In FIG. 7 and FIG. 8 the tube 144Aand the rod 144B are tensioned against one another with the casings 150,151 such that maximum strength is achieved, as already mentioned abovewith respect to FIG. 4 to FIG. 6. Flexing of the bearing bolts 144 isgreatly minimised. The bearing bolt 144 can thus be produced on the onehand from a tube 144A, which forms the bearing position, and on theother hand from a rod 144B with a thread and head. The length of one ofthe tubes 144A defines the separation of the casings 150, 151 andtherefore the size of the outer rotary part 14. If, for example, a screwas a rod 144B is pushed through the hole of the tube 144A and the onecasing 151, for example, such that it projects at the other end of thetube 144A with its thread into the threaded hole of the other casing150, the tube 144A can be screwed very tight with the casings 150, 151,that is to say the tube 144A is stressed under pressure, the screw asthe rod 144B under tension. This is a tensioned construction whichpromises high stability and is very favourable in production. Thebearing position, that is to say the tube 144A, would be effectivelysecured against unintentional twisting by the tensioned join.

This tube/rod fixing described can be employed not only with respect tothe casings 150, 151 but also in the case of the discs 142 of FIG. 4 toFIG. 6.

According to a fourth example the annular bars 141 extend outwardsbeyond the shell plane of the outer rotary part 14. The bearing bolts144 for the outer rotary part 14 here can be arranged as hitherto, butalso on the outside of the outer rotary part 14. In this case the shellplane of the outer rotary part 14 is perforated at the correspondingpoints in order to create space for the coupling mechanisms 18. Thebearing bolts 144 must be secured against unintentional twisting, sothat it is ensured that the bearing pairing of the coupling mechanism 18is called on. The continuously variable transmission 10 is otherwiseconstructed as in the first example.

As shown in FIG. 9 and FIG. 10 in a transverse and longitudinal section,according to a fifth example the inner rotary part 13 is produced fromone or more metal sheets 131, 132 in a wound construction with highperformance adhesives and optionally with tensile stress. A hollow space133 thus forms in the middle of the inner rotary part 13. The woundconstruction can also be laminated in composite technology with variousmaterials of steel/carbon. A closing pipe 134 can be pushed over thiscomposite construction and glued in order to give a suitable surface tothe sprags/bearings, described later, for the coupling mechanism 18.

According to FIG. 9 the composite construction in a spiral constructionforms a wavy part as the inner rotary part 13. In FIG. 9 the spiral isshown as an open spiral for better illustration since an intermediatespace is present in each case between the metal sheets 131, 132. Inreality, however, in the inner rotary part 13 the metal sheets 131, 132are wound layer on layer, so that no intermediate space is presentbetween the metal sheets 131, 132.

An alternative to the production of parts from steel by means of themilling/turning technique is thus presented here, a construction usingcomposite materials and the laminating technique thereof beingdescribed. For example, steel sheets which are rippled or wavy at rightangles to the winding direction can be used. The metal sheets 131, 132can be loaded with a particular tensile stress in the winding directionhere.

Furthermore, during the winding operation a liquid laminating adhesivecan be introduced between the layers. The most diverse materials ofglass/carbon fibres can also be co-laminated in. When the windingoperation has ended and the laminate has set, the pretensioning of thewinding technique can be removed and the blank can be pushed into asteel tube with laminating resin, allowed to set and then baked to thefinal strength in an oven. The tube 134 here would have the task e.g.for the inner rotary part 13 of forming a highly tempered runningsurface for the clutches of an inner coupling module described in thefollowing. The advantage of this technique is to ensure the comparablestrength of the structural elements with a higher elasticity and a lowerspecific weight than, for example, high-alloy steel.

The coupling mechanism 18 can be guided axially on the inner rotary part13 or between the bearing plates of the housing 19. All the couplingmechanisms 18 consequently are adjacent axially to their neighbour attheir end to the inner rotary part 13, so that only the couplingmechanisms 18 furthest removed must be guided axially at their end tothe inner rotary part 13. At their end to the outer rotary part 14 thecoupling mechanisms 18 do not have to be guided axially in the supportin the outer rotary part 14. However, the coupling mechanisms 18 can beguided axially in the support in the outer rotary part 14.

FIG. 11 and FIG. 12 show diagrams of the construction of the couplingmechanisms 18 according to a sixth example. The coupling mechanism 18comprises an outer coupling module 180, an inner coupling module 181, anouter bearing 182 for the outer coupling module 180, and a bearing 183which serves as an inner bearing for the outer coupling module 180 andas an outer bearing for the inner coupling module 181. The outer andinner coupling module 180, 181 are pivotable with respect to one anotherby an angle α, as shown by a rotary arrow. The coupling mechanism 18here is configured such that for the angle α is <180°, as shown in FIG.11. By this means the coupling mechanism 18 cannot fold over in thedirection of an arrow 184 into the state shown in FIG. 12. FIG. 11 hereshows the state of maximum eccentricity of the coupling mechanism 18. Incontrast, the state of FIG. 12 is an inadmissible state.

In order to achieve such a coupling mechanism 18, according to a firstvariant the eccentricity of the coupling mechanism 18 can be limitedwith the adjustment device, in accordance with the adjusting element 15and/or adjustment drive device 20, or between the housing 19 and secondbearing and guiding module 12, with “stops”. Alternatively or inaddition, according to a second variant stops for the coupling mechanism18 can also be formed in the articulated axes of at least one of theouter and inner bearings 182, 183, 184, 185. However, the former variantis preferred, since an undefined operating state can form in the secondvariant. Possibilities for articulated stops for the inner and outercoupling modules 181, 180 are:

-   -   outer coupling module 180 through articulated axis or bearing        182 stops at the outer rotary part 14,    -   inner and outer coupling module 181, 180 have stops in the        vicinity of the articulated axis or bearing 183 such that the        angle α in FIG. 11 cannot become greater.

In addition a combination of the abovementioned possibilities for thearticulated stops is possible.

As described above, the coupling mechanisms 18 are arranged on therotary parts 13, 14 via sprags. The sprags can be produced entirely fromhard metal, e.g. tungsten, silicon carbide etc.

Furthermore, a clutch of the coupling mechanisms 18 can be constructedas a disc brake which can be controlled externally. The implementing ofan additional coupling mechanism 18 per coupling unit renders possible aforced control of the braking device resulting from the kinematics. Thecontrol, such as opening and closing of the brake, must take place inadvance of the coupling mechanism 18 in question.

FIG. 13 shows a diagram of the construction of the coupling mechanisms18 according to a seventh example. The coupling mechanism 18 herecomprises cranked bearing bolts 182A, 182B and 183A, 183B. Consequently,the outer bearing 182 for the outer coupling module 180 comprises thetwo parts 182A, 182B, the other bearing 183, which serves as an innerbearing 184 for the outer coupling module 180 and as an outer bearing185 for the inner coupling module 181, comprises the two parts 183A,183B. The inner and outer coupling modules 181, 180 therefore do notmove around one pivotal point, as in FIG. 11 and FIG. 12, but around twopivotal points. The angle α here is in each case constant in the parts182B, 183B. By this means also the coupling mechanism 18 cannot foldover into an inadmissible state. The sense and purpose of the couplingmechanism 18 shown in FIG. 13 is to deform the sinus function of amovement of a coupling mechanism 18 such that the ideal of a rectangularfunction is approached, with the aim of maintaining the rotary movementuniformly at the output drive.

FIG. 14 and FIG. 15 show two views of an inner coupling module 181 inlightweight construction according to an eighth example. As illustratedin FIG. 14, the inner coupling module 181 has the form of a double cam.The inner coupling module 181 is configured symmetrically to thedot-dash central line. At an internal opening 181A the inner couplingmodule 181 has a running surface 181B for a sprag set or a support.

FIG. 15 shows in a side view that the inner coupling module 181 is not asolid part, but has several slots 181C. The slots 181C can be produced,for example, by correspondingly screwing in the inner coupling module181 radially to the inner opening. The inner coupling module 181 canalso be constructed in disc form in order to produce the slots 181C.

As shown in FIG. 16 in a section A-A of FIG. 14, carbon fibres 181D canbe wound with lamination under pretension into the slots 181C. However,the carbon fibres are not necessarily to be provided. Furthermore, amass balancing bolt 180A can be provided on the inner coupling module181, which can balance the mass of a bearing bolt 181E of the outercoupling module 180. By this means the mass is exactly the same on bothsides of the dot-dash central line in FIG. 16. The bearing bolt 181Ebelongs gravimetrically to the inner coupling module 181 and is guidedin a bearing casing 181F. The opposite mass balancing bolt 180Arepresents the exact counter-weight over the symmetry plane/

Overall, by the measures shown in FIG. 15 and also FIG. 16 in thepresent example a significant weight reduction results in the innercoupling module 181 compared with a solid component. Moreover, the innercoupling module 181 can very advantageously be balanced by the massbalancing bolt 180A.

Furthermore, according to this example the outer coupling module 180 canbe constructed as illustrated in FIG. 17 in a section view and in FIG.18 in a side view. The outer coupling module 180 is connectedrotatably/pivotably, similarly to a knee joint, to the inner couplingmodule 181 with the bearing bolt 181E of the inner coupling module 181via openings 180D of the outer coupling module 180, as can also be seenfrom FIG. 16. The outer coupling module 180 is preferably constructedsuch that its weight in the region L1 is equal to its weight in theregion L2. The line between L1 and L2 preferably goes exactly throughthe bearing central point. Furthermore, in the outer coupling module 180a central bar 180B connects two arms 180C, which demarcate the outercoupling module 180 on two opposite sides. Profiles of the outercoupling module 180, such as, for example, its central bar 180B and/orits arm(s) 180C, can also be, for example, tubular, double T-shaped etc.

The outer coupling module 180 is thus also very advantageously balancedby the mass distribution described.

With the outer and inner coupling module 180, 181 described above acomplete mass balancing of the inner and outer coupling module can beensured. As a result the rotating coupling functional elements canperform the high rotational speeds required for the continuouslyvariable transmission 10.

The outer coupling module 180 can be produced by the deep-drawing and/orsheet metal pressing technique. If no chambers are formed by annularrings in the outer rotary part 14, the outer coupling module 180 istherefore not tapered, it then has a rectangular base shape in planview.

In the outer coupling module 180 in the cheeks or arms 180C oil feedbores which realise the lubricant feed to the bearing positions of thebolt 181E of the inner coupling module 181 can be provided radially inrecesses, such as, in particular, grooves etc. around a bearing bore180D. Radial openings, in particular through bores, can furthermore bearranged in the bearing casing 181F of the bearing bolt 181E of theinner coupling module 181. The outer coupling module 180 can also beguided axially on the bearing bolt 29 (FIG. 3) itself instead of in achamber of the outer rotary part 14. An axial guiding of the innercoupling modules 181 on the inner rotary part 13 is not absolutelynecessary.

Since the clutch elements (sprags) must also be capable of transferringenergy, FIG. 19 to FIG. 22 indicate advantageous embodiment variants forthis.

FIG. 19 shows a lower foot region of the sprag element 31A lying on theinner rotary part 13. The lower foot region of the sprag element 31A isconcave in shape, whereas the inner rotary part 13 is convex in shape.Here, the radius of the concave curvature of the lower foot region ofthe sprag element 31 is greater than the radius of the convex curvatureof the inner rotary part 13.

In the embodiment variant of FIG. 20, on the other hand, the lower footregion of a sprag element 31B is spherical in shape. The lower footregion of the sprag element 31B and the inner rotary part 13 are thusconvex in shape here. In this embodiment variant only a slight linearcontact is thus present from the lower foot region of the sprag element31B and the inner rotary part 13. In the embodiment variant of FIG. 20the contact area of sprag element 31B and inner rotary part 13 istherefore subject to a greater wear than in the embodiment variant ofFIG. 19.

In FIG. 21 and FIG. 22 reaching of high rotational speeds is achieved byindividual spring mounting of the sprag elements 34. In addition oralternatively, reaching of high rotational speeds can be achieved causedby centrifugal force or flinging force, for example, by sprag geometry,centre of gravity, pressing in an annular gap, as illustrated in FIG. 21and FIG. 22. Furthermore, as already mentioned above the inner and outercoupling module 181, 180 and the outer rotary part 14 should be as lightand strong as possible.

FIG. 21 shows a spring 33 which presses a sprag 34 with a shank 34A inthe direction of the arrows 35. The spring 33, which can press the sprag34 into the desired position, can be supported on a cage 39 whichreceives the sprag 34. As a result the sprag 34 is pressed into anannular gap 36 between, for example, the inner rotary part 13 and theinner coupling module 181. During power transmission the powertransmission arises via the lowering action. The range of the shank 34Aleads to the centrifugal force, in addition to the force of the spring33, pressing the sprag 34 into the annular gap 36. FIG. 21 moreovershows the arrangement of the sprag 34 with respect to the input drivedirection 40 and the output drive direction 50.

In FIG. 22 one end of the sprag 34 is arranged with holding elements 37in a sprag shoe 38. The spring 33 here is formed in an S-shape. Withthis variant the surface area of the sprag 34 can be increased in orderto reduce wear. The end of the sprag 34 on the sprag shoe 38 has aradius either smaller than or equal to the radius of the correspondingreceiver for the end of the sprag 34 in the sprag shoe 38.

Since the outer coupling module 180 of the continuously variabletransmission 10 can perform three-dimensional movements, the functionalcomponents for the radial support are also to be supported axially.Several possibilities for this are described in the following.

FIG. 23 to FIG. 26 each show different variants for an axial securing ofa bolt or a shaft 50 on a plate-shaped element 51, such as, for example,a disc 142. Such an axial securing can be employed, for example, for thebearing bolts 180A and/or also for the inner rotary part 13 etc.

According to the variant of FIG. 23 the shaft 50 and the disc 51 arefixed to one another by means of a welded joint 52 in the form of, forexample, weld points, a weld seam etc.

According to the variant of FIG. 24 the shaft 50 has on its one end apeg 53 and on its other end a peg 54. The pegs 53, 54 are each twistedinto an opening of a disc 51. The peg 53 here has a right-hand thread.The peg 54 has a left-hand thread.

According to the variant of FIG. 25 the shaft 50 is arranged in anopening of the disc 51 and pressed therein. For this, in particular, thecircumference of the shaft can be somewhat larger than the diameter ofthe opening of the disc 51.

According to the variant of FIG. 26 the shaft 50 has on each of its twoends an opening 55. A plate screw 56 can be screwed into each of theopenings 55, as shown on the left-hand side in FIG. 26.

FIG. 27 to FIG. 30 each show various variants for securing againsttwisting of a bolt or a shaft on a plate-shaped element 51 such as, forexample, a disc 142 (FIG. 5 and FIG. 6). Such a radial securing againsttwisting can be employed, for example, for the inner rotary part 13 orthe bearing bolts 180A etc. The radial securing against twisting can becombined with the axial securing according to FIG. 19 to FIG. 22.

According to the variant of FIG. 27 in the disc 51 teeth 57 are providedin an opening of the disc 51. If the shaft is toothed correspondingly,it can engage with the disc 51 and in this way be secured againsttwisting with respect to the disc 51.

According to the variant of FIG. 28 the opening 58 is configured to fita splined shaft.

According to the variant of FIG. 29 the opening 59 is flattened, theshaft being configured accordingly.

According to the variant of FIG. 30 and FIG. 31 the disc 51 has on itssurface in the radial direction of the disc 51 axial raised parts 60,not all of which are provided with reference symbols in FIG. 30. Theraised parts 60 protrude out of the disc to a predetermined extent, asillustrated in FIG. 31.

FIG. 32 shows a preferred embodiment of a lubricant supply of thecontinuously variable transmission 10. This provides a forced lubricantsupply between the inner rotary part 13 and the coupling mechanisms 18,particularly preferably between the inner rotary part 13 and the innercoupling module(s), by means of a pump. A lubricant stream in the axialdirection along the shell surface of the inner rotary part 13 existshere. In addition, a first guiding channel 194 is provided within thebearing and guiding module 11, preferably within the bearing plate 112of the inner rotary part 13, to the bearing position of the inner rotarypart, through which the lubricant is introduced via a first guidingcasing 196, that it to say an interface of the stationary part (such asthe housing) to the rotatable part (inner coupling module 181), to theshell surface of the inner rotary part 13. Particularly preferably, thisregion is given by the annular gap of the inner rotary part 13 and thebore of the coupling mechanism 18, preferably of the inner couplingmodule 181. The lubricant is now delivered in an axial direction alongthe inner rotary part 13. Between the coupling mechanisms 18 arranged inseries in the axial direction of the inner rotary part 13 a definedlubricant loss can advantageously be intended, which preferably suppliesthe axial support and/or the internal machine element with lubricant bycentrifugal force. Furthermore, preferably a second guiding channelwithin the other bearing and guiding module, preferably within the otherbearing plate of the inner rotary part 13, and particularly preferably asecond guiding casing as an interface of the stationary part to therotatable part are provided, which particularly preferably compared withthe first guiding channel and the first guiding casing is at theopposite end, in the axial direction, of the inner rotary part 13. Thesecond guiding channel is advantageously provided so that the exitinglubricant can flow in the corresponding bearing of the housing. Throughthe second guiding channel 198, the return flow of the lubricant isprovided or the lubricant is sucked up. The lubricant stream along theshell surface of the inner rotary part 13 is limited at both ends of theinner rotary part 13 by in each case a shaft sealing ring 136.Preferably, a lubricant stream is thus provided only in the region ofthe inner rotary part 13 which is in the housing 19.

Preferably, on the axial support of a coupling mechanism 18 an annularbar can be mounted enclosing this, which projects into a groove of anadjacent coupling mechanism 18.

In a particularly preferred embodiment of the lubricant supply of thecontinuously variable transmission 10 rings which run into one anotherand are slightly spaced are employed on the coupling mechanisms 18, orhydraulic seals or mechanical seals are provided.

In a further preferred embodiment of the lubricant supply overlappingsealing rings 138 are provided between in each case two couplingmechanisms 18 adjacent in the axial direction, which seal off possibleintermediate spaces between the adjacent coupling mechanisms 18 from thelubricant stream on the shell surface of the inner rotary part 13.Particularly preferably, the thickness of these sealing rings 138 tapersin the direction of the lubricant stream.

Any desired combinations between the so-called leakproof lubricantsupply, in which no substantial loss of lubricant, for example by exitof the lubricant for lubrication of the internal machine elements and/orthe coupling mechanism 18, occurs, and a lubricant supply with loss oflubricant are also conceivable. Such a combination could be, forexample, the arrangement of sealing rings 138 between only some couplingmechanisms, but not between all coupling mechanisms.

Advantageously, by the in these preferred embodiments of the lubricantsupply no nozzles positioned in a stationary manner in the internalmachine element or simultaneously rotating nozzles are necessary.However, stationary nozzles could also be provided instead and/or inaddition.

Advantageously, a fine filter element is furthermore provided in thesuction line of the pump which ensures the lubricant stream of thelubricant supply.

Moreover, depending on the vertical or horizontal alignment of thecontinuously variable transmission, that is to say depending on whetherthe axial direction of the inner rotary part 13 is aligned vertically orhorizontally during start-up of the continuously variable transmission,corresponding bores are provided for the pump, for sucking up thelubricant, on the container in which the lubricant collects, inparticular, during operation of the pump. The bores here are preferablyalways on the lubricant line of the lower part of the continuouslyvariable transmission, in which the lubricant collects due to gravity.

All the configurations of the continuously variable transmission 10described above can be used individually or in all possiblecombinations. In particular, the features of the examples describedabove can be combined as desired or if required omitted. In addition,the following modifications in particular are conceivable. The partsshown in the figures are in diagram form and can deviate in preciseconfiguration from the forms shown in the figures, as long as thefunctions thereof described above are ensured.

The inner rotary part 13 can be used as an input drive or output drive.The outer rotary part 14 consequently can also be used as an outputdrive or input drive.

For each part of the continuously variable transmission 10 there is thepossibility of employing all types of steels, coatings, hard metals,composite materials, carbon-glass fibres etc.

The applicant reserves the right to claim all the features disclosed inthe application documents as essential to the invention if individuallyor in combination they are novel with respect to the prior art. It isfurthermore pointed out that features which in themselves may beadvantageous have also been described in the individual figures. Theperson skilled in the art can see directly that a particular featuredescribed in a figure may also be advantageous without adopting furtherfeatures from this figure. The person skilled in the art can furthermoresee that advantages may result by a combination of several featuresshown in individual or in different figures.

1. A continuously variable transmission having an outer rotary part, aninner rotary part which is arranged in the outer rotary part such thatthe inner and/or the outer rotary part are rotatable relative to oneanother, several coupling mechanisms for coupling the inner and outerrotary part with one another, an adjustment device for eccentricadjustment of the inner and outer rotary part relative to one another, apump for delivering a lubricant into the transmission along a shellsurface of the inner rotary part, and sealing elements which arearranged on the inner rotary part in the coupling mechanisms, or nozzlesfor delivering a predetermined amount of lubricant to the particularcoupling mechanism.
 2. The continuously variable transmission of claim1, furthermore having a housing for receiving the continuously variabletransmission, wherein the pump for delivering the lubricant is arrangedin a circulation into and/or from the housing.
 3. The continuouslyvariable transmission of claim 1, wherein the outer rotary part hasdiscs which are spaced apart by bearing bolts for the couplingmechanisms.
 4. The continuously variable transmission of claim 1,wherein the outer rotary part has two casings fixed to one another,which are spaced apart by bearing bolts for the coupling mechanisms. 5.The continuously variable transmission of claim 1, wherein one of thecoupling mechanisms has: an inner coupling module which is arranged onthe inner rotary part and an outer coupling module which is arranged onthe outer rotary part.
 6. The continuously variable transmission ofclaim 5, wherein the inner coupling module has a mass balancing bolt forbalancing a mass of a bearing bolt of at least one coupling module, withwhich bearing bolt the inner and outer coupling module can be fixed toone another rotatably/pivotably.
 7. The continuously variabletransmission of claim 5, wherein the inner coupling module has at leastone slot for receiving carbon fibres wound by lamination withpretension.
 8. The continuously variable transmission of claim 1,wherein the inner rotary part has at least one wound metal sheet.
 9. Thecontinuously variable transmission of claim 8, wherein the at least onewound metal sheet is arranged in a tube.
 10. The continuously variabletransmission of claim 1, wherein a lower end of a sprag element isconcave in construction, the sprag serving to support one of thecoupling mechanisms on the inner rotary part.
 11. The continuouslyvariable transmission of claim 1, wherein a bearing position for anadjusting element of the adjustment device is arranged in the axialdirection centrally on a bearing and guiding module, which serves tosupport the outer rotary part.
 12. The continuously variabletransmission of claim 5, wherein the outer and inner coupling module canbe swivelled by an angle with respect to one another and this angle isless than 180°.
 13. The continuously variable transmission of claim 1,wherein the eccentricity of the outer rotary part relative to the innerrotary part is limited with the adjustment device with stops.
 14. Thecontinuously variable transmission of claim 1, wherein the eccentricityof the coupling mechanism between a housing and a bearing and guidingmodule which serves to support the outer rotary part is limited bystops.
 15. The continuously variable transmission of claim 1, wherein alubricant stream exists in the axial direction along the shell surfaceof the inner rotary part, by which a lubricant supply is providedbetween the inner rotary part and the coupling mechanisms.